DE69631111T2 - Method and device for cooling a fluid stream and drying gas cooling - Google Patents

Abstract

A gas flow Aa, which is saturated with vapor of water or of other volatile liquid and in which large amount of minute drops of water or of other volatile liquid float, is sent in a group of small channels 4, of a cross-flow type or counter-flow type heat exchanger 3, and a fluid flow B is sent in the other group of small channels 5. Sensible heat is exchanged between the gas flow Aa and the fluid flow B. The minute drops of the volatile liquid floating in the gas flow Aa vaporize by the rise of the temperature of the gas flow Aa, and the fluid flow B is refrigerated by the vaporization of the minute drops. When water is used as the minute drops of volatile liquid floating in the gas flow Aa, a large amount of cold wind can be supplied cheaply, and when a liquid having low boiling point such as methanol is used as the minute drops of volatile liquid, the refrigeration temperature can be lowered. <IMAGE>

Description

The present invention relates to a method and an apparatus for cooling a fluid by heat exchange between fluids, like something between air and air or between a liquid and a gas, and as an application thereof relates to a method and an apparatus for desiccant cooling gas such as air.

For cooling gas, such as air or a liquid, is common a freezer has been used which cooling by Heat of vaporization from Fleongas (chlorofluorocarbons: trademark of duPont, USA) performs, that by compressing liquid Refrigerant such as fleece gas is liquefied using a compressor. In such a freezing device for emitting compression heat of Fleongas a cooling tower used the cooling by doing that fleon gas is passed through a spiral hose on which Downward water stream is left, and besides by heat of vaporization of water flowing through leave air in the opposite direction.

With the usual air conditioning it is necessary to extract air of comfortable temperature and humidity, being it also both temperature and humidity are required processing of outside air high temperature and high humidity. If fleon gas compressed by a compressor in such air conditioning energy consumption is great and the destruction of the Airborne ozone layer from fleon gas is a serious disadvantage. Moreover is in a cooling tower consumes a lot of energy.

Aa, mentioned above, by unbound heat of fluid B over the heat exchanger evaporate, and around the gas A method or device accordingly the preamble of claim 1 and claim 13 is from US-A-4,901,919.

The present invention aims to achieve this ab, a method and an apparatus for cooling a fluid, such as of gas, such as air, and a liquid using a heat exchanger and specify an application of them to air comfortable temperature and moisture or gas of low temperature and low humidity feed continuously by desiccant cooling of gas, such as air, using little energy and without Use of fleon gas.

To high temperature fluid B in accordance with the present invention through unbound heat exchange between low temperature gas A and the high temperature fluid B below Use of a cross flow heat exchanger or other heat exchanger to cool in which two types of fluids of different temperature are not are in direct contact with each other, low temperature gas A in the saturated Condition with volatile Liquid vapor, such as water vapor, transferred and then in the state in which a large amount of tiny drops of water or other liquid drops becomes an even distribution to achieve d. that is, to put an air flow Aa in the state in which a great Amount of tiny drops of liquid floated in the gas. This is transferred into a flow passage of the heat exchanger and the high temperature fluid B is transferred into the other flow passage, around the tiny drops of liquid M in the gas Aa mentioned above by unbound heat of the Fluids B over the heat exchanger to evaporate and the gas Aa by the heat of vaporization of the liquid drops to cool whereby the fluid B through heat exchange between this chilled Gas stream Aa and the fluid B is cooled with high efficiency.

The invention accordingly provides a method for cooling a fluid, according to which a gas stream A is converted into a gas stream Aa, which is saturated with volatile liquid vapor, and in which a large amount of misty tiny liquid drops M of the volatile liquid float, and in which the Gas flow Aa through a flow passage ( 4 ) of a heat exchanger ( 3 ) is directed, which has several flow passages ( 4 . 5 ), starting from a position above the heat exchanger ( 3 ), and for cooling the fluid B through the other flow passage ( 5 ) of the heat exchanger ( 3 ) is conducted so that appreciable heat of the fluid B is transferred to the gas stream Aa, while the gas stream Aa is a flow passage ( 4 ) of the heat exchanger ( 3 ) to increase the temperature of the gas stream Aa, so that a large amount of tiny liquid drops M floating into the gas stream Aa is evaporated, and the temperature of the gas stream Aa is continuously reduced by the heat of vaporization of the liquid drops to the fluid B continuously cooling by noticeable heat exchange between the gas stream Aa and the fluid B, characterized in that the diameter of each drop of the volatile liquid is not greater than 280 μm.

1 Fig. 12 is an overview view and a partially enlarged view thereof showing an example of the method and the device for fluid cooling according to the present invention;

2 shows a perspective view of an example of a cross-flow heat exchanger and a partially enlarged view thereof;

3 shows a sectional view of another example of the method and the device for fluid cooling according to the present invention;

4 Fig. 4 is an explanatory view of still another example of the device of the fluid cooling method according to the present invention;

5 shows a psychometric diagram of fluid cooling data provided in 4 is shown;

6 shows an explanatory view of a contrasting example of the method and the device for fluid cooling;

7 shows a psychometric diagram showing data of fluid cooling, which in 6 is shown;

8th Fig. 4 is an explanatory view of still another example of the method and the device for fluid cooling according to the present invention;

9 shows a psychometric diagram showing data of fluid cooling, which in 8th is shown;

10 Fig. 12 is an explanatory view showing data of fluid cooling according to the present invention and using an aqueous methanol solution;

11 Figure 12 shows a psychometric diagram of cooling data using an aqueous methanol solution;

12 Fig. 4 is an explanatory view of still another example of the method and the device for fluid cooling according to the present invention;

13 shows a perspective view of a countercurrent heat exchanger;

14 shows a perspective view of an example of a heat exchanger that combines counterflow and crossflow;

15 shows a perspective view of another example of a cross-flow heat exchanger;

16 Fig. 12 is an explanatory view of an example of the method and the device for refrigerant cooling of gas according to the present invention;

17 Fig. 4 is an explanatory view of another example of the method and the apparatus for refrigerant drying gas according to the present invention;

18 Fig. 4 is an explanatory view of still another example of the method and the apparatus for refrigerant drying gas according to the present invention;

19 shows a vertical section of a device for cooling water in accordance with the present invention, applied to a refrigerator or a cooling device;

20 shows a perspective view of a device for cooling water, which in 19 is shown, with part broken away for purposes of illustration; and

21 shows a vertical section of a device for cooling air in accordance with the present invention, applied to the refrigerator or the cooling device.

Detailed description of the preferred embodiments

In accordance with the invention with claim 1 becomes more volatile mist a gas stream A to saturate it added to form a gas stream Aa in which a large amount of foggy tiny drops of water M floated. This gas flow Aa is through a flow passage of a heat exchanger with multiple flow passages and for cooling of the fluid B is through a further flow passage of the heat exchanger conducted such that the unbound heat of the fluid B on the gas stream Aa transferred will while the gas flow Aa through a flow passage of the heat exchanger passes to increase the temperature of the gas stream Aa. If the saturation ratio of the Gas phase part (for example the relative humidity in the Case that the fleeting liquid Water is) becomes smaller, a large amount of tiny water drops M that float in the gas stream Aa evaporates, and the temperature of the gas stream Aa falls continuously by heat of vaporization of the liquid drops to the fluid B to cool continuously. This creates a gas stream Aa in which a large amount of tiny drops of liquid M floated, through unbound heat exchange with the fluid B in the passage of the heat exchanger heated and fluid B is cooled by evaporation of the tiny drops of water M, which extracts the heat of evaporation and by lowering the temperature of the gas Aa.

example 1

Flat flat materials 1 and corrugated flat materials 2 with a wavelength of 3.0 mm and a wave height of 1.6 mm, both of which are made of sheet metal such as aluminum sheet or synthetic resin sheet such as polyester, are layered alternately and in such a way that the direction of the waves of the corrugated flat materials 2 crosses after each one (expansion) step, and they are connected to each other in such a way that a cross-flow heat exchanger 3 is obtained as in 2 shown. When small concavities and convexities are formed by rays and the like exerted on the flat material surface, the flat materials become hydrophilic and the surface becomes larger at the same time.

Aluminum sheet can be made hydrophilic the sheet in an aqueous sodium phosphate, Sodium hypochlorite, chromic acid, Phosphoric acid-, oxalic acid or sodium hydroxide solution is soaked or soaking in boiling water in a short time to reveal hydrophilic substances the surface of the aluminum sheet.

As a cross-flow heat exchanger 3 is a combination of flat flat materials 1 and corrugated flat materials 2 shown as an example. If small waves are formed in the flat sheet material part, the surface area is further increased, whereby the heat exchanger efficiency is increased. If the surfaces of the flat sheet material 1 and the corrugated sheet 2 made black, radiation and absorption of radiant heat increase, which improves the heat exchanger efficiency. If the sheet material surface is changed to a hydrophilic one, the ventilation of gas in small channels can be prevented from being reduced by the pressure drop due to the water drops in the event that the fluid B is air or another gas.

As in 2 and 3 shown is the cross-flow heat exchanger 3 chosen such that a group of small channels 4 runs almost vertically, while the other group of small channels 5 runs almost horizontally. As in 3 shown are a channel 8a and 8b at the flow inlet 4a or at the flow outlet 4b the group of small channels 4 intended. The channel 8a is with an aerator Fa and a water spray nozzle 6 Mistake. A channel 9a and a channel 9b are at a flow inlet 5a and a flow outlet 5b the group of small channels 5 ( 2 ) intended. The channel 9a is equipped with a fan F. In the drawing, Va forms a valve which determines the spray volume of the water spray nozzle 6 regulated.

A water spray nozzle or device 6 (hereinafter referred to as water spray nozzle) is preferably used to evenly distribute water drops so that they are as small as possible, such as in the form of an air atomization nozzle. Water drops are preferably as small as possible and measure about 10 μm. When the largest diameter of the water droplets sprayed through the air mist nozzle is set to about 280 µm, the diameters of about 70% of the water drops are smaller than 100 µm, and the effect of the present invention is fully demonstrated.

An air atomizing nozzle is used for spraying using water and air, and sprayed water drops become smaller when the water and air are pressurized. The size of the water spray drops can be easily influenced by the air pressure, and it is desirable to generate a pressure greater than 3 kgf / cm ² . A nozzle can only be used using liquid.

The effect or mode of operation of the cooling device will now be explained. As in 3 shown is the above water spray nozzle 6 used for an outside air or indoor air flow A to spray a large amount of tiny water drops onto the air flow A such that the temperature drops due to heat of vaporization of the water drops and the relative humidity increases. In addition, it is transferred to an air flow Aa in which a large amount of tiny water drops M float, and the air flow Aa is fed into numerous flow passage inlets 4a of the heat exchanger 3 by emitting pressure from the fan Fa.

When a high temperature air flow B in the flow passage 5a of the heat exchanger 3 is transmitted by the fan F, on the other hand, the air flow Aa extracts unbound heat from the high-temperature air flow B through a partition 1 (please refer 2 ) of the flow passage, while the air flow Aa the flow passage of the heat exchanger 3 interspersed to increase the temperature of the air flow Aa. The relative humidity of the air flow Aa thereby decreases, and a large amount of tiny water drops M contained in the air flow Aa evaporate to the lower temperature of the air flow Aa by the heat of vaporization of the water drops, and the high-temperature air flow B becomes through the partition 1 cooled.

The cooling principle of this cooling device is explained in more detail below. The vapor pressure of the liquid is larger in the liquid drop state than in the state when the liquid maintains a horizontal surface, and the smaller the liquid drop diameter, the larger the liquid vapor pressure. This phenomenon is expressed by the Kelvin formula below Log (pr / p) = 2δM / ρRT

In this formula, p is the vapor pressure on the horizontal surface, pr is the vapor pressure of the drop of liquid with the radius r, M is the molar mass, δ is the surface tension, ρ is the Liquid density, R is the gas constant and T is the absolute temperature.

The smaller the radius of the water drops, the faster they evaporate and the stronger the cooling effect. In the process of evaporating sprayed water drops M in the heat exchanger 3 the diameter of the water drops M also becomes smaller. The smaller the diameter of the what drops M becomes, the higher the vapor pressure. The evaporation of the water drops M is therefore accelerated. That is, tiny drops of water M evaporate in the heat exchanger 3 in an extremely short time with evaporation heat removed.

In the case of water at 18 ° C and in accordance with the above formula, the vapor pressure increases by 0.1% compared to that in the state that the water surface becomes flat when the radius of the water drops becomes 1 µ, and by about 10% when the radius of the water drops becomes 10 μm. The vapor pressure is almost doubled if the radius of the water drops is further reduced to 1 μm. When air in which a large amount of tiny water drops M floats into the heat exchanger 3 is transferred, as mentioned above, a phenomenon is observed, according to which the water drops M in the heat exchanger 3 evaporate quickly.

Tests were carried out using this cooling device. As in 4 an air flow A with a temperature of 25.9 ° C., an absolute humidity of 8.05 g / kg and a relative humidity of 39% is shown through a water spray nozzle 6 directed to reduce its temperature to 17.5 ° C, and at the same time to convert it into an air flow Aa with 100% humidity, in which a large amount of tiny water drops M float. This airflow Aa is in an inlet 4a of small channels 4 transferred that are almost vertical in the heat exchanger 3 are arranged with an air flow of 2 m / s. On the other hand, the high temperature air flow B with a temperature of 70.6 ° C, an absolute humidity of 10.44 g / kg and a relative humidity of 5.2% is in a flow inlet 5a transmitted by small channels that are almost horizontal in the heat exchanger 3 are arranged, the air flow rate being 2 m / s through the fan F. The little channels 4 do not necessarily have to be exactly vertical: it is sufficient if water drops in the air float through or move through. 5 shows a psychometric chart of air cooling in this case, and Table 1 shows the test result.

Table 1 (with spray nozzle)

Unbound heat exchange is performed between the high temperature air stream B and the air stream Aa, and the temperature of the air stream Aa is continuously lowered by the evaporation of tiny water droplets floating in the air stream Aa as mentioned above, thereby lowering the temperature of the air stream B without increase the absolute humidity, while achieving a comfortable air temperature of 18.6 ° C, an absolute humidity of 10.44 g / kg and a relative humidity of 78%, which is used as supply air or supply air SA. The air flow Aa becomes an air flow Ab with a temperature of 30.7 ° C and a relative humidity of 100% by passing through the heat exchanger 3 is directed. This air flow Ab is emitted or emitted into the atmosphere.

The unbound heat exchange efficiency η _t in this case becomes 97.9%, as shown by the formula (1) in Table 1, which shows that the heat exchange efficiency is very high. In the formula (1), B, SA, Aa show the temperature of the respective air. The amount of water drops that are sprayed is about 8 to 15 liters per hour. The throughput of air flows A and B in this case is approximately 180 m ³ / h. The heat exchanger size is 0.25 m × 0.25 m = 0.0625 m ² , based on the area, the surface of its inlets 4a . 5a is 0.0625 m ² and the channel opening rate is about 40%. The cross-sectional area of the small channels is therefore 0.0625 m ² × 40% = 0.025 m ² , and since the wind speed 2 m / s, the wind volume is 0.025 m ² × 2 m / s = 180 m ³ / h.

For comparison, test data are for the case using the same cross-flow heat exchanger as in Example 1, but without using a water spray nozzle in an air flow for cooling in 6 shown in Table 2 and in the psychometric diagram in 7 applied.

Table 2

In the formula (2), B, Ba and A the temperature of the respective air.

An air flow A with a temperature of 22.3 ° C becomes an air flow Starting with a temperature of 62.0 ° C through unbound heat exchange and a high temperature air flow B having a temperature of 67.2 ° C becomes an air flow Ba with a temperature of 36.0 ° C through unbound heat exchange. The absolute humidity changes not in airflow A and airflow B.

The unbound heat exchange efficiency η ₁ in this case is 69.5%, as shown in Table 2 by the formula (2). When water is sprayed, the unbound heat exchange efficiency is 97.9. If no water is sprayed, it is 69.5. Spraying water therefore increases the heat exchange efficiency by about 30%. The other experimental conditions are the same as in the case of Example 1 with water spray.

Example 2

Using this cooling device similar to that in 8th shown, air with a temperature of 25.7 ° C, an absolute humidity of 12.0 g / kg and a relative humidity of 59.0% is converted into an air flow A with a wind speed of 2 m / s. This air flow is through a water spray nozzle 6 directed to obtain an air flow Aa with a temperature of 20.2 ° C, a relative humidity of 100%, in which a large amount of mist-like tiny drops of water float evenly.

This airflow Aa is in an inlet 4a of small channels 4 a heat exchanger transferred. On the other hand, high-temperature air to be cooled to 34.2 ° C, with an absolute humidity of 14.41 g / kg and a relative humidity of 43%, is transferred in an air flow B with a wind speed of 2 m / s, which is then in an inlet 5a of small channels 5 of the heat exchanger is transferred. Unbound heat exchange is carried out between the high temperature air flow B and the air flow Aa and the air flow B is cooled air SA with a temperature of 20.6 ° C, an absolute humidity of 14.41 g / kg and a relative humidity of 95%. This air flow Aa becomes an air flow Ab with a temperature of 25 ° C and a relative humidity of about 100%, which is emitted or emitted into the atmosphere. The psychometric diagram in this case is in 9 shown and the test data are listed in Table 3.

Table 3 (with spray nozzle)

As shown in the drawing, heat of vaporization of water drops in the air stream Aa is transferred to the air stream B through a partition to lower the temperature of the air stream B without changing the absolute humidity, as shown in the psychometric diagram, along the ho Rizontal line or X-axis of the psychometric diagram until it reaches the point SA (20.6 ° C), and the temperature of the air flow Aa increases until it reaches the point Ab along the relative humidity line of 100%. The unbound heat exchange efficiency in this case is 97.1, as shown by the formula (3) in Table 3, and roughly corresponds to the unbound heat exchange efficiency of Example 1. That is, when the temperature of the fluid B drops , the temperature of the supply air or supply air SA is 20.6 ° C, which temperature is suitable for air conditioning, by reducing the amount of water sprayed. The amount of water sprayed is about 8 l / h.

Example 3

As in 1 are shown in addition to that in 3 shown and explained in Example 1, a water tank D is provided, which receives water droplets that are emitted together with an air stream Ab, a recirculation device for water, which is stored in the tank D, ie, a pump P, a water pipe 10 , an electric valve Va and a water level regulator, ie, a water level float Vs, a water level sensor Se, an electric valve Vb, a spray amount regulator of a water drop sprayer 6 , ie, a thermocouple Ta, a thermocouple Tb, an electrical signal amplifier C and an electrical valve Va. In the drawing, parts are given the same reference numerals as in FIG 3 not explained because they correspond to the parts that are in 3 are explained in Example 1.

A water pipe is provided 10 which water in a tank D in a water spray nozzle 6 recirculated, and it is provided with a pump P and an electric valve Va in the middle. A water supply pipe 11 is provided on the water tank D. A water level float Vs floats on the water surface 13 in the water tank D. An electromagnetic on / off valve Vb in the water supply pipe 11 and a water level sensor Se are connected. As in the enlarged view of part Q of 1 shown, a change in the water level is detected by the water level float Vs and the water level sensor Se. When the water level is up 13L falls, the electromagnetic valve Vb opens to supply water. When the water level is up 13H rises, the electromagnetic valve Vb closes to stop the water supply.

A water temperature sensor for gas flow A is provided, such as a thermocouple Ta on the upstream side of the water spray nozzle 6 , another temperature sensor, such as a thermocouple Tb in the fluid B. The thermocouples Ta and Tb are connected to an electrical signal amplifier C. The temperature difference between these two thermocouples Ta and Tb is recorded and fed into the electrical signal amplifier C. When the temperature difference becomes larger, the electric valve Va is operated to increase the sprayed water volume, and when the temperature difference becomes smaller, the sprayed water volume is decreased. The flow rate of the air flow Aa is increased by increasing both the water spray volume and the power output of the fan FA.

If in this case the amount sprayed from the water spray nozzle 6 is too large, tiny drops of water collect on the inner wall of the small channels 4 of the heat exchanger 6 and drip down without being completely evaporated. The surface of the water flow is extremely small compared to that of the tiny water drops, and there is too little water evaporation due to the heat extracted from the high temperature air flow B as a contribution to cooling. The temperature of the air flow Aa can therefore not be lowered completely, which makes a complete drop in the temperature of the high temperature air flow B impossible. If water is sprayed such that minute water drops M are contained in the air flow Aa evenly and in a required amount, the cooling efficiency becomes high and water can be saved.

Example 4

Instead of in the spray nozzle 6 water used (boiling point 100 ° C) can be a volatile organic liquid such as ethanol (boiling point 78.3 ° C), methyl acetate (boiling point 56.3 ° C) and methanol (boiling point 64.7 ° C) or mixed liquids such volatile organic liquid with water can be used.

Tiny particles of drying agent silica gel are on both sides of a partition 1 blown up and stuck there, and a corrugated flat material or sheet 2 with a wavelength of 3.4 mm and a wave height of 1.7 mm (see 2 ), both consisting of an aluminum sheet with a thickness of 25 μm, and both alternately stacked on top of each other to form a cross-flow heat exchanger 3 to get a size of 250 mm × 250 mm × 250 mm. One in 10 Cooling device shown is using this heat exchanger 3 created.

10 shows the data for a case using this device and a 45% aqueous solution of ethanol instead of water used for the spray nozzle 6 in Examples 1 and 2. In In this case, its boiling point drops because an aqueous solution of methanol is used instead of water, and the temperature of air stream A was reduced by 95.5 ° C to 14.9 ° C after spraying the aqueous methanol solution (air stream Aa).

The low temperature side SA of 17.2 ° C was obtained by heat exchange of this air flow Aa with 14.6 ° C and a high temperature air flow B with 51.3 ° C. In order to obtain a lower temperature air SA, it is therefore more favorable to spray liquid with a low boiling point than to spray only water. The psychometric diagram of 11 shows the state changes of the air flow B in the air flow SA and the air flow A in the air flow Aa and the air flow Ab as mentioned above.

Example 5

This in 12 The device shown consists of the device explained in Example 1, in which a device for recirculating a gas stream Ab is additionally provided, which comes out of the outlet 4b from the heat exchanger 3 is discharged to a highly humid gas stream Aa, using a humidifier 7 upstream of the water spray nozzle 6 is provided. In 5 are the outlet 4b of the heat exchanger 3 and the fan Fc through a channel 8e connected, and the fan Fc and the flow passage of the highly humid air flow Aa are connected to the duct 8d connected. A diverging duct K for entering outside air OA, if necessary, is with part of the duct 8e connected.

The humidifier 7 is provided with a valve V halfway through a water supply pipe Wp so that water can be supplied when humidification is required. As a humidifier 7 come into consideration one of the ultrasonic type and one using several woven fabrics which are immersed in water or soaked in water.

A gas flow Aa is through the heat exchanger 3 passed and exhaust from the outlet 4b is recirculated by a fan Fc to be used as the gas flow Ac. This gas flow Ac is through a humidifier 7 passed, if necessary, and transferred into a gas stream Aa in which a large amount of tiny water drops M through a spray nozzle 6 floated to recirculated and into the heat exchanger 3 to be transferred.

In 12 is the channel 8e with a cooling part Co in the middle and numerous ribs Fe are on the outside of the channel 8e provided that are covered with a cover. A fan Fd is connected to this. By cooling the fin Fe by the fan Fd, fluid Ab becomes in the channel 8e cooled to cool and condense moisture in the highly moist fluid Ab. The condensed water is stored in the tank D and water in the tank is discharged and transferred back to the water spray humidifier from time to time through a valve Vc.

The fluid cooling method according to the present The invention has so far been based on an example of a cooling method for air using a cross flow heat exchanger. Of course can also be used for cooling of a different gas than for Air or other liquid than for water be used.

Instead of the above-mentioned cross-flow heat exchanger, a diagonal-cross-flow heat exchanger, a countercurrent heat exchanger, as in 13 shown, or used, which is a combination of a counterflow heat exchanger and a crossflow heat exchanger, as in 14 shown. Both in the counterflow heat exchanger, which in 13 is shown as in one which is a combination of a counterflow heat exchanger and a crossflow heat exchanger as in 14 a gas stream Aa in which tiny water droplets float and a fluid B pass through small channels in the direction of arrows in the drawings, and they are discharged as gas stream Ab or fluid SA in order to carry out unbound heat exchange between the fluids Aa and B. , A cross-flow heat exchanger with numerous spacers can also be used 12 . 12 ... between flat plates 1 . 1 ... is created so that the direction of a spacer crosses every step or step rectangularly, as in 15 and a heat exchanger, which is a countercurrent heat exchanger or a combination of a countercurrent heat exchanger with a cross-flow heat exchanger, similar to the honeycomb laminate discussed above.

Example 6

As in 16 shown are a cross flow heat exchanger 3 with 250 mm × 250 mm × 250 mm and a spray humidifier 6 provided and a dehumidifier rotor 14 is in front of the heat exchanger 3 arranged. The dehumidifier rotor 14 is made of a honeycomb laminate with which an adsorbent or a hygroscopic agent is combined, in a cylindrical shape with a diameter of 320 mm and a width of 200 m. The dehumidifier rotor 14 is in an absorption zone 16 and a reactivation zone 17 by separating elements 15 . 15 ' divided. The rotor is provided with a flow passage through a channel (in the Drawing not shown) provided, as shown by the arrows B → HA → SR. The dehumidifier rotor 14 is continuously rotated and operated at a speed of 16 rpm in the direction of the arrow in the drawing. Outside air A with a temperature of 34.0 ° C, an absolute humidity of 14.4 g / kg and a relative humidity of 43.1% is converted into an air flow B by a fan Fb, and the air flow B becomes the adsorption zone 16 of the dehumidifier rotor 14 transmitted at a wind speed of 2 m / s.

The moisture contained in the air stream B is adsorbed and removed by this dehumidifier to obtain a dry air stream HA. Thereupon the dry air flow HA enters the inlet 5a horizontal small channels 5 of the heat exchanger 3 transfer. Outside air OA is heated to about 80 ° C by heater H and into the reactivation zone 17 of the dehumidifier rotor 14 transferred in the direction of the arrow in the drawing as reactivation air RA. The dehumidifier 14 is dehumidified and reactivated in the reactivation zone 17 and the reactivation air RA is discharged or emitted into the air as moist discharge air EA.

On the other hand, if the air flow A with a temperature of 26 ° C and a relative humidity of 58% through the spray humidifier 6 was humidified to achieve a relative humidity of 100%, the temperature of the air flow Aa became 17.0 ° C. Water is also sprayed onto or into this air flow Aa in such a way that tiny drops of water float in large numbers in it. The air flow Aa is in the flow inlet of the heat exchanger 3 transfer.

The dry air flow HA, mentioned above, passes through the heat exchanger 3 enforced an unbound heat exchange with the air flow Aa in which minute water drops float in large numbers, and it was caused by heat of vaporization of minute water drops in the air flow Aa in the heat exchanger 3 cooled, which is similar to the explanation of Example 1, in order to obtain comfortable supply air or supply air SA with a temperature of 20.5 ° C., an absolute humidity of 4.5 g / kg and a relative humidity of 30%.

The example given above shows that by dehumidifying the outside air at a temperature of 34 ° C., an absolute humidity of 14.4 g / kg and a relative humidity of 43.1 and by directing the obtained dry air, its temperature increases was by heat of moisture adsorption, and its moisture was reduced by the heat exchanger 3 , cooled dry air with a temperature of 20.5 ° C, an absolute humidity of 4.5 g / kg and a relative humidity of 30%. By using this air for air conditioning purposes, it can be suitably dehumidified to achieve comfortable air conditions.

Of course, a two-cylinder Dehumidifier filled with a hygroscopic agent a cylindrical or Kathabar-type dehumidifier (trademark), which is provided by Kathabar Company USA, as a dehumidifier in addition to a rotary dehumidifier used in this Example is used.

Example 7

This example explains a method for dehumidification by a dehumidification rotor after cooling a High temperature air at 70 ° C through a heat exchanger.

As in 17 shown is a spray dehumidifier 6 on the top of a cross-flow heat exchanger 3 provided, and a dehumidifying rotor 14 is behind the heat exchanger 3 intended. If water through a spray dehumidifier 6 is sprayed on or in outside air OA with a temperature of 26.0 ° C, its absolute humidity is 12.2 g / kg and its relative humidity 85% by a fan Fa until their relative humidity reaches 100% and the temperature of the Outside air OA drops to 17.5 ° C. In addition, water is sprayed onto or into this air and the air flow Aa obtained, in which a large amount of tiny water particles floats, is passed through a flow passage 4a of the heat exchanger 3 directed.

On the other hand, an air flow B with a temperature of 70 ° C., an absolute humidity of 14.4 g / kg and a relative humidity of 7% is introduced into the inlet 5a of the heat exchanger 3 transmitted by the fan Fb at a wind speed of 2 m / s. The air flow B becomes a low temperature air flow Ba through the unbound heat exchange in the heat exchanger.

The absolute humidity of the air flow Ba is essentially the same as that of the air flow B. The air flow HA becomes an air flow Ab with a temperature of 30 ° C. and a relative humidity of approximately 100% at the outlet of the heat exchanger 3 after using the heat exchanger 3 has flowed through and is discharged into the outside air. The dehumidifier rotor 14 is rotated and actuated at 16 rpm in the direction of the arrow in the drawing.

The cooled air flow Ba, which is mentioned above, is in the adsorption zone 16 this dehumidifier rotor 14 transferred to obtain a dry air flow HA with a temperature of 55 ° C, an absolute humidity of 4.5 kg / kg and a relative humidity of 5% by adsorbing / dehumidifying moisture. How the dehumidifier rotor works 14 is as explained in Example 5. Although dehumidification of the high temperature air by the adsorption system is extremely difficult, a simple effective and effective dehumidification to obtain cooled dry air when the dehumidifier is used after cooling by a heat exchanger before the dehumidifier as shown in this example.

Example 8

The air flow HA obtained in Example 7 has a temperature of 55.0 ° C and a relative humidity of 5%. Its temperature is too high and its relative humidity is too low for normal air conditioning. This example therefore serves to additionally flow this air flow HA through a second heat exchanger 3b to lead to supply air or supply air SA with a temperature and humidity that are suitable for air conditioning.

As in 18 is shown, a high temperature air flow B through the cross flow heat exchanger 3a and the dehumidifier rotor 14 directed as in Example 7 to obtain an air flow HA. Since the procedure is the same as in Example 7, there is no need to repeat the explanation. The second cross-flow heat exchanger 3b is behind the dehumidifier rotor 14 provided, that is, in the flow passage of the air flow HA flowing out of the process air outlet. A spray dehumidifier 6b is upstream of a flow passage 4 of the second heat exchanger 3b provided as in Example 7 above. Because the operation of this second heat exchanger 3b is the same as that of the heat exchanger 3 the example 7 given above does not need to be explained.

On the other hand, a dry air flow HA that passes through the adsorption zone 16 of the dehumidifier rotor 14 was directed into a flow passage inlet 5a small channels 5 transferred horizontally in the heat exchanger 3b are arranged. The performs an unbound heat exchange with a cooled air flow Aa, which contains a large amount of tiny drops of water, in order to provide a comfortable supply air or supply air SA with a temperature of n20.5 ° C, an absolute humidity of 4.5 g / kg and a relative humidity of 30%. When regulating the air conditioning conditions of the supply air SA, the amount of water sprayed on the air flow Aa is controlled to change the temperature of the supply air SA. If the humidity of the supply air SA is too low, the reactivation temperature of the dehumidifier rotor is lowered 14 to reduce the dehumidification efficiency of the dehumidifier rotor 14 while increasing the humidity of the supply air SA to carry out a comfortable air conditioning as desired.

In Examples 6 to 8 above explained can be by spraying on the air flow Aa of liquid with a low boiling point, such as ethanol, methyl acetate and methanol instead of water, used in spray humidifier, the temperature of the supply air flow or supply air flow SA is additionally reduced become.

An ultrasonic nebulizer can also be used can be used as a fog generator in each example. Next to an air mist nozzle can a fluid nozzle, that does not use air, is used as a water spray device or nozzle become. In the above Examples were the moisture one stage by a spray humidifier transferred to 100% and at the same time became a big one Amount of tiny water particles made to float in it. Can also spray humidifier be provided in several stages, so that the humidification in one first stage until the relative humidity reaches 100%, and a large amount tiny water particles are floated in the second step. It is essential that air is passed through a heat exchanger, whose relative humidity is 100%, and in which a large amount floated by tiny water particles of about 10 μm in diameter.

A heat exchanger used as an example in the above Examples shown was one formed by layering a corrugated sheet and a flat sheet in an alternating manner. However, the present invention is not on such a heat exchanger limited; rather, all are suitable which have a plurality of flow passages whose surface is large enough is, such as a heating tube, provided with flow passages at both ends is the numerous heat exchange fins exhibit.

Example 9

In 19 denotes the reference number 18 a known freezer with a compressor or compressor (not shown in the drawing) inside and the reference number 19 denotes a heat exchanger, of which a flow passage 20 is in a spiral while another flow passage 21 jacket-like, the spiral flow passage 20 is provided surrounding.

Hot fleon gas or other refrigerant flows from or out of a compressor or into a flow passage 20 of the heat exchanger 19 and cools or cool water that is in the other flow passage 21 of the heat exchanger 19 flows.

Another flow passage 21 of the heat exchanger 19 is with a flow passage of a cross-flow heat exchanger 3 through a pipe 22 connected to which a circulation pump 23 intended is. That is, the heat exchanger 19 and the cross-flow heat exchanger 3 are selected so that cooling water circulates between them in an airtight state. In the drawing, reference numbers indicate 9a . 9b Chambers.

The reference number Fa denotes a blower, the suction side of which is open to the atmosphere, and the discharge side of which is at the upper end of a chamber 24 connected is. The lower end of the chamber 24 is with the further flow passage inlet 4a of the cross-flow heat exchanger 3 connected. The further flow passage outlet of the cross-flow heat exchanger 3 opens into the atmosphere or is open to it.

A spray device 6 is in the chamber 24 provided the relative humidity of the air in the chamber 24 to 100%, and at the same time to create such a state that a large amount of tiny drops of water float, that is, a fog state. As a spray device 6 For example, an air spray nozzle is used with which a pressure booster pump P for water and a compressor 25 are connected.

The reference numeral D denotes a water tank, which is under the cross-flow heat exchanger 3 provided and with a drain pipe 10 is provided.

As in 20 shown is this cross-flow heat exchanger 3 arranged so that the axis of a group of its small channels 4 runs almost vertically, and that the further group of its small channels 5 runs almost horizontally, and a chamber 24 is at a flow inlet 4a of the channels 4 provided and with a fan Fa and a water spray nozzle 6 Mistake. The chambers 9a . 9b are at the flow inlet 5a provided and at a flow outlet 5b of the small channels 5 and they're with a pipe 22 connected.

The operation of the structure explained above will now be explained. A cooling device using a cross-flow heat exchanger 3 will now be explained. A fan Fa is operated to generate a gas flow A on or in the water drops by a water spray device 6 be sprayed to obtain a gas stream Aa. The amount of water sprayed should be greater than the amount of vaporization by spraying. A portion of the water drops are then sprayed to evaporate, removing heat of vaporization to lower the temperature of the gas stream Aa entering the chamber 24 is transmitted. At the same time, the air gets into the chamber 24 , ie, the gas stream Aa has a relative humidity of 100% and comes into a state in which a large amount of tiny water particles float in the air, ie, in the fog state.

This air, in which a large amount of tiny drops of water float, then enters a group of small channels 4 of the cross-flow heat exchanger 3 , If a freezer 18 is in operation, has refrigerant in a flow passage 20 of the heat exchanger 19 flows, high temperature and performs a heat exchange with water, which in the further flow passage 21 of the heat exchanger 19 is directed.

That in the further flow passage 21 of the heat exchanger 19 drained water is pumped through 23 circulated and into the further group of small channels 5 of the cross-flow heat exchanger 3 through the pipe 22 and the chamber 9a transfer. An unbound heat exchange is carried out between the one group of small channels 4 and the other group of small channels 5 through a partition 1 , This means that cooling water, which through the further group of small channels 5 is cooled by the gas stream Aa flowing through a group of the small channels and at the same time the gas stream Aa which is the one group of the small channels 4 interspersed, warmed.

Thereupon the relative humidity of the gas stream Aa, the channels 4 interspersed, lower than 100%, and a large amount of tiny water particles contained in it evaporates by removing heat of vaporization and cooling the gas stream Aa.

In such a process, the temperature of the gas stream Aa, which is a group of small channels 4 enforced, kept almost constant at a low value. The cooling water, which is the further group of small channels 5 is therefore continuously implemented in full and in full length of the small channels 5a of the heat exchanger 3 cooled and its temperature is kept almost constant.

If in this case the spray amount from the water spray device 6 is too big, tiny drops of water collect on the partition in the small channels 4 of the cross-flow heat exchanger 3 and cling to each other to form large water drops and water flows, which, with much smaller surfaces compared to the tiny water drops, cannot completely lower the temperature of the gas flow Aa by heat extracted from the refrigerant, which is why the temperature of the refrigerant is not complete can be lowered. If the tiny drops of water are sprayed to contain a little more than the minimum required, the cooling efficiency is high and, more importantly, water can be saved.

Water drops in the small channels 4 of the cross-flow heat exchanger 3 not evaporate, are collected or stored in the water tank D and out of the drain pipe 10 discharged. As stated above, the amount of water coming from the water sprayer 6 is sprayed, almost iden table to the amount of evaporation in the small channels 4 of the cross-flow heat exchanger 3 , The amount of water accumulated in the water tank D is therefore small, and there is no problem if it is discarded as a whole. From the water spray device 6 sprayed water is therefore used without being recirculated, which prevents algae growth.

In the above examples, water was used as the liquid to be cooled. It is also contemplated to add freeze preventive agents, such as ethylene glycol, to the water to about 50 volume percent, taking into account the risk of freezing in the winter, or adding anti-corrosion agents to the corrosion of the heat exchanger 19 and the cross-flow heat exchanger 3 to prevent.

Example 10

21 shows another example of a cooling device of a freezer in this example. The difference for example from 19 is the following: In Example 9, which in 19 Water is shown through the further group of small channels 5 of the cross-flow heat exchanger 3 passed; in this example an air flow from a fan F through the further group of ducts 5 of the cross-flow heat exchanger 3 directed.

That is, F denotes a blower that is connected to the inlet of the chamber 9a connected is. The outlet of the chamber 9a is with the admission of another group of small channels 5 of the cross-flow heat exchanger 3 connected. The outlet 5b of the small channels 5 is with the inlet of the chamber 9b connected and the outlet of the chamber 9b is with a radiator 26 connected.

A pipe 27 is provided such that refrigerant from the freezer 18 through the radiator 26 is directed. Since the structure of this example is the same as in Example 9 except for the difference mentioned above, further explanation is unnecessary.

In this example, air penetrates the further group of small channels 5 of the cross-flow heat exchanger 3 by the fan F, is cooled and reaches the radiator 26 , Hot refrigerant from the freezer 18 is in the radiator 26 through the pipe 27 transferred to emit heat of the refrigerant. Air through the small channels 5 has penetrated into this radiator 26 transfer.

In other words, the radiator 26 cooled by the air flow while moving the further group of small channels 5 of the cross-flow heat exchanger 3 penetrates, and the efficiency is much better than in the case of direct cooling from outside air.

A cross-flow heat exchanger was used in the experiments carried out by the applicant 3 corresponding to that of Example 9 as in 19 shown, used: air was blown through the small channels 4 of the cross-flow heat exchanger 3 passed through the blower Fa at a speed of 2 m / s when the outside air temperature was 35 ° C and the relative humidity was 39%, and 12 l / h of water was passed through the sprayer 6 sprayed. Thereupon the temperature of the air was from the cross-flow heat exchanger 3 to the radiator 26 transferred, 18.6 ° C and the cooling effect of the refrigerant was extremely high.

In this example, a cooling device a freezer according to the present Invention installed in front of a radiator of the air conditioning device that is already provided, and the efficiency of a freezer an air conditioner that is already installed and a refrigerator and the like can be done by simple and easy procedures elevated or be improved.

With the invention achievable effect

The present invention is structured as explained above and its principle is to pass a gas flow for cooling a mist-like gas flow Aa with a relative humidity of 100%, in which a large amount of tiny water droplets float uniformly, through the flow passage of a heat exchanger, which has a plurality of fluid passages, and to pass a fluid B, which is to be cooled, such as air or water, through the further flow passage, whereby the gas stream Aa contacts the fluid B with the tiny drops of water floating therein, a partition being provided between them to heat the gas stream Aa to lower the relative humidity of the gas stream Aa, and to evaporate the tiny drops of water, the heat of vaporization of which cools the gas stream Aa and also cools the fluid B through the partition. It is characteristic of the invention that it is able to regulate the cooling level for the fluid B by controlling the amount of water by the water spray device 6 is sprayed. By increasing the amount of water sprayed as the temperature difference between the gas stream Aa and the high temperature air stream B becomes larger, the fluid Aa increases the cooling level of the high temperature air stream B in proportion to the temperature difference between the fluid Aa and the high temperature air stream B, and the air stream B can be adjusted to one cooled almost constant temperature. Dry, cooled air can also be easily obtained by combining this cooling device with a dehumidifier.

As explained in Example 1, a cross flow heat exchanger was used 3 with a spray humidifier 6 Mistake. An air flow Aa with a large amount of tiny floating water drops as air flow for cooling purposes cools a high temperature air flow B with an extremely high unbound heat exchange efficiency of approximately 97 to 100%. If the same cross-flow heat exchanger as in Example 1 is used and no sprayer and no humidifier is used for an air flow for cooling purposes, the unbound heat exchange efficiency is 63% as shown in the contrast example in Example 1. It can be seen from this that the heat exchange efficiency in fluid cooling according to the present invention is extremely high.

The energy consumption for this heat exchange needed will be about 250 W as operating energy for a fan. The thermal energy, the one for cooling of the fluid B is required, however, is one and a half to several ten times as big as energy consumption, and this value increases when the temperature of fluid B increases.

This cooling device for a fluid can be used for cooling gas and also for refrigerant cooling of gas by adding a dehumidifier, as in 6 to 8th shown, so for air conditioning. Since the operating costs in this case are extremely low, as stated above, it is therefore not necessary to use room air for repeated recirculation to cool the desiccant in a closed room: desiccant air conditioning can therefore continue to be carried out with a continuous intake of fresh outside air. Increase in dangerous gas, such as carbon dioxide, in room air can thereby be completely prevented while providing a comfortable room.

There is also no environmental problem since free gas, as in air conditioning according to the prior art, is not is used and it will have an excellent hygienic effect Viewing angle because there is no need for a compressor insert and hot Air through waste heat, through which bacteria or mold can be generated.

Claims (29)

Method for cooling a fluid, according to which a gas stream A is converted into a gas stream Aa which is saturated with volatile liquid vapor and in which a large amount of misty tiny liquid drops M of the volatile liquid float and in which the gas stream Aa flows through a flow passage ( 4 ) of a heat exchanger ( 3 ) is directed, which has several flow passages ( 4 . 5 ), starting from a position above the heat exchanger ( 3 ), and for cooling the fluid B through the other flow passage ( 5 ) of the heat exchanger ( 3 ) is conducted so that appreciable heat of the fluid B is transferred to the gas stream Aa, while the gas stream Aa is a flow passage ( 4 ) of the heat exchanger ( 3 ) to increase the temperature of the gas stream Aa, so that a large amount of tiny liquid drops M floating into the gas stream Aa is evaporated, and the temperature of the gas stream Aa is continuously reduced by the heat of vaporization of the liquid drops to the fluid B continuously cooling by noticeable heat exchange between the gas stream Aa and the fluid B, characterized in that the diameter of each drop of the volatile liquid is not greater than 280 μm. Cooling process a fluid according to claim 1, wherein the amount of tiny drops of liquid M floating in the gas stream Aa according to the change the temperature difference between the gas stream Aa and the fluid B. changed becomes. Cooling process of a fluid according to claim 1, wherein the flow rate of the gas stream Aa, in which tiny drops of liquid Float M according to the change in temperature difference is changed between the gas stream Aa and the fluid B. Cooling process of a fluid according to any one of claims 1 to 3, wherein the gas stream A is converted into a gas stream, that by fleeting liquid vapor saturated is, and that more volatile mist Moreover is added to the gas stream in order to convert it into the gas stream Aa, in which is a big one Amount of tiny drops of liquid M swim up. A method of cooling a fluid according to any one of claims 1 to 4, wherein a gas stream Aa containing a large amount of liquid liquid vapor is discharged from the outlet ( 4b ) a flow passage ( 4 ) of the heat exchanger ( 3 ) is carried out to the side of the inlet ( 4a ) this flow passage of the heat exchanger is returned, and that a mist of a volatile liquid is added to the gas stream in order to convert the gas stream into a gas stream Aa in which tiny liquid drops M float to be used in the circulation. Cooling process of a fluid according to any one of claims 1 to 5, wherein the volatile liquid is water, the fleeting organic liquid or a mixture of liquids out of volatile organic liquid and water is. A method of cooling a fluid according to any one of claims 1 to 6, in which the volatile liquid is passed through a gas / liquid mixing nozzle ( 6 ) is sprayed. Cooling process of a fluid according to one of claims 1 to 7, in which it is the fluid B is a gas. Method for cooling a fluid according to one of Claims 1 to 8, in which the fluid B is passed through a dehumidifying device ( 14 ) is dehumidified before or after it passes through the heat exchanger ( 3 ) is conducted. A method of cooling a fluid according to claim 9, in which the fluid B is a gas and in which two gas streams Aa are provided and in which one of the gas streams Aa in a flow passage ( 4 ) from each of the two heat exchangers ( 3a . 3b ) is passed, and the gas stream B in turn through the other flow passage ( 5 ) of the first heat exchanger ( 3a ), the dehumidifier ( 14 ) and the other flow passage ( 5 ) of the second heat exchanger ( 3b ) is conducted. A method of cooling a fluid according to claim 9 or 10, wherein the dehumidifier ( 14 ) is a rotary dehumidifier. Cooling process of a fluid according to any one of claims 9 to 11, wherein the dehumidifier is a desiccant dehumidifier. Device for cooling a fluid, comprising a mist formation device ( 6 ) for adding a volatile liquid to a gas stream A in order to convert it into a gas stream Aa which is saturated with volatile liquid vapor and in which a larger amount of misty tiny drops M of the volatile liquid float, and a heat exchanger ( 3 ) with multiple flow passages ( 4 . 5 ), the gas flow Aa from a position above the heat exchanger ( 3 ) through a flow passage ( 4 ) and a fluid B to be cooled is passed through the other flow passage ( 5 ) is conducted so that the gas stream Aa dissipates noticeable heat of the fluid B, while the gas stream Aa passes through a flow passage ( 4 ) passes through the heat exchanger so that a large amount of tiny liquid drops M floating in the gas stream Aa is evaporated and the temperature of the gas stream Aa decreases continuously by the heat of vaporization to continuously cool the fluid B, characterized in that the Diameter of each drop of volatile liquid is not larger than 280 μm. A fluid cooling device according to claim 13, wherein means ( 7 ) for introducing volatile liquid vapor upstream from a misting device ( 6 ) is intended for volatile liquid. A fluid cooling device in accordance with claim 13, wherein a channel ( 8d . 8e ) and a blower (Fc) are provided which block a gas flow Ab which emerges from an outlet ( 4b ) of the heat exchanger ( 3 ) is carried out to the inlet side ( 4a ) of the heat exchanger ( 3 ) conducts to circulate a gas stream Aa for cooling. A fluid cooling device according to any one of claims 13 to 15, wherein a heat exchanger ( 3 ) is a cross flow heat exchanger, a diagonal cross flow heat exchanger, a counter flow heat exchanger or a counter flow / cross flow combination heat exchanger which consists of a honeycomb laminate which is alternately formed by laminating flat sheets and corrugated sheets. A fluid cooling device according to any one of claims 13 to 15, wherein a heat exchanger ( 3 ) is a cross-flow heat exchanger, a diagonal cross-flow heat exchanger, a counter-current heat exchanger or a counter-current / cross-flow combination heat exchanger, which is formed by laminating surfaces with numerous spacers between the surfaces. Fluid cooling device according to any one of claims 13 to 17, wherein the surface of the heat exchange element ( 1 . 2 ) is hydrophilic. A fluid cooling apparatus according to claim 16 or 17, wherein minute particles on the wall surface of a flow passage ( 4 . 5 ) of a heat exchanger ( 3 ) stick firmly. A fluid cooling device according to claim 19, the tiny particles being an adsorbent. A fluid cooling device according to any one of claims 13 to 15, the device further comprising a desiccant dehumidifier ( 14 ) for dehumidifying fluid B before or after the fluid passes through the heat exchanger ( 3 ) is conducted. A fluid cooling device according to claim 21, wherein the dehumidifying means ( 14 ) in the upstream side of the high temperature gas flow B into the heat exchanger ( 3 ) is provided. A fluid cooling device according to claim 21, wherein the dehumidifying means ( 14 ) in the downstream side of the high temperature gas stream B into the heat exchanger ( 3 ) is provided. Device for cooling a fluid according to claim 21, wherein the fluid B is a gas, and wherein two gas flows Aa are provided, and wherein two heat exchangers ( 3a . 3b ) with multiple flow passages ( 4 . 5 ) are provided, the one gas stream Aa through a flow passage ( 4 ) from each of the two heat exchangers ( 3a . 3b ), and wherein the gas stream B is sequential through the other flow passage ( 5 ) of the first heat exchanger ( 3a ), the dehumidifier ( 14 ) and the other flow passage ( 5 ) of the second heat exchanger ( 3b ) is conducted. Device for cooling a fluid according to one of claims 21 to 24, wherein the dehumidifying device ( 14 ) is a rotary dehumidifier. A fluid cooling device according to claim 25, wherein the dehumidifier is a desiccant dehumidifier is. Device for cooling a fluid according to claim 13, comprising a heat exchanger ( 19 ), which is a source of waste heat ( 20 ) a freezer ( 18 ) is assigned, whereby the fluid B, as soon as it has cooled, enters the heat exchanger ( 19 ) is directed to the heat exchange source ( 20 ) Exchange heat. A fluid cooling device according to claim 27, wherein the fluid B is selected from the group consisting of water and a liquid mixture containing water consists. Device for cooling a fluid after a of claims 13 to 28, wherein the fluid B is a gas.